JP4425469B2 - Thrust bearing device for gears - Google Patents

Thrust bearing device for gears Download PDF

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Publication number
JP4425469B2
JP4425469B2 JP2000569146A JP2000569146A JP4425469B2 JP 4425469 B2 JP4425469 B2 JP 4425469B2 JP 2000569146 A JP2000569146 A JP 2000569146A JP 2000569146 A JP2000569146 A JP 2000569146A JP 4425469 B2 JP4425469 B2 JP 4425469B2
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Japan
Prior art keywords
gear
shaft
thrust bearing
bearing device
contact
Prior art date
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Expired - Fee Related
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JP2000569146A
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Japanese (ja)
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JP2002524704A (en
Inventor
ヨゼフ、ベイダー
ユルゲン、ラウター
シュテファン、レナー
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ZF Friedrichshafen AG
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ZF Friedrichshafen AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/30—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for axial load mainly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19233—Plurality of counter shafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19242—Combined gear and clutch

Description

【０００１】
本発明は、特許請求の範囲請求項１の上位概念部分に記載の歯車用軸受装置に関する。
【０００２】
はすば歯車付き変速機において、はすばによってひき起こされる軸方向力によって、歯車が荷重される。特に荷重分配用に多数の副軸を備えた変速機の場合、その軸方向力のために、種々の運転状態において、入力軸およびこの入力軸に支持された主軸との間の範囲に配置された第２常時かみ合い歯車において、この歯車の軸受が変形される、という問題が生ずる。
【０００３】
荷重分配のために同一形状の多数の副軸を備えた変速機において、入力軸あるいは主軸に僅かな半径方向隙間をもって配置された歯車は、副軸上に配置された歯車に、半径方向に支持されている。しかし、これらの歯車がそれぞれの軸上における軸方向位置から移動しないようにするために、これらのを歯車を軸方向に支持する必要がある。しかし、はすばからの軸方向力は、歯車の位置を、軸方向に移動しようとする。
【０００４】
主に次の３つの運転状態に区別される。
【０００５】
まず、第１の危険のない運転状態において、トルクが、変速機の入力軸から、第１常時かみあい歯車を介して、副軸に伝達される。そのスラスト軸受は、比較的一様に、荷重される。
【０００６】
しかし、他の２つの運転状態において、軸方向力が、特に不利に作用する。まずその１つの運転状態は、トルクが、変速機の入力軸から、第２常時かみ合い歯車を介して、副軸に伝達されるような運転状態である。トルクはそこから、主軸に結合される任意の歯車に伝達される。もう１つの問題ある運転状態は、変速段を形成するために、入力軸が、第１および第２の常時かみ合い歯車を介して主軸に結合され、両方の常時かみ合い歯車を介してトルクが流れるときに、生ずる。
【０００７】
その前者の運転状態において生ずる軸方向力は、第２常時かみ合い歯車を、入力軸から軸方向に離れる方へ動かすように、作用する。後者の運転状態で生ずる軸方向力は、第２常時かみ合い歯車を、入力軸の方へ軸方向に移動するように、作用する。そのいずれの場合も、軸方向力は、第２常時かみ合い歯車のスラスト軸受を傾斜させる。
【０００８】
ＤＥ１９６３３２８１号明細書において、第２常時かみ合い歯車に対するスラスト軸受が知られている。そこで利用されているディスクは、両側がそれぞれ、ころ軸受によって包囲されている。軸方向力は、ディスクを傾斜させ、周辺ホルダの形をしたころ軸受を損傷し、その結果、軸受の寿命をかなり縮める。
【０００９】
本発明の課題は、ころ軸受が傾くという問題を除去した軸受装置を提供することにある。
【００１０】
この課題は特許請求の範囲の請求項１に記載の手段によって解決される。本発明の有利な実施態様は従属請求項に記載されている。
【００１１】
本発明に基づいて、第１軸および第２軸が、同軸的に位置すると共に互いに異なった回転数で回転でき、第１および第２の両軸の回転中心線の方向における軸方向力をバランスするために歯車が配置され、この歯車が、第１スラスト軸受と第２スラスト軸受との間に設けられている手段上、特にディスク上に配置されているような歯車式変速機における、第１軸と第２軸との間の範囲にある歯車に対する軸受装置において、第１軸と第１スラスト軸受との間および第２スラスト軸受と第２軸との間に、それぞれディスクが設けられ、これらのディスクは、それぞれの軸と線で接触するようになっており、前記ディスクは、基本状態においては前記回転中心軸に対して垂直な姿勢を取る一方で、当該垂直な姿勢を中心として一方側傾斜姿勢と他方側傾斜姿勢との間で揺動（sway）するように構成されている、ことによって解決される。
なお、補正前の表現では、第１軸および第２軸が、同軸的に位置すると共に互いに異なった回転数で回転でき、第１および第２の両軸の回転中心線の方向における軸方向力をバランスするために歯車が配置され、この歯車が、第１スラスト軸受と第２スラスト軸受との間に設けられている手段上、特にディスク上に配置されているような歯車式変速機における、第１軸と第２軸との間の範囲にある歯車に対する軸受装置において、第１軸と第１スラスト軸受との間および第２スラスト軸受と第２軸との間に、それぞれディスクが設けられ、これらのディスクが、それぞれの軸と線で接触し、その接触線を中心として円錐変形運動をするように構成する、ことによって解決される。ここで円錐変形運動とは、平らなディスクが、軸方向力の作用のもとで、円錐状の環状板の形に変形することを意味し、これは、平らなディスクを皿ばねとほぼ同じ輪郭に変形することを意味する。
【００１２】
本発明の有利な実施態様において、第１軸および第２軸に、半径Ｒのラジアル面をした接触部位が形成され、これらの接触部位が、ディスクと第１、第２軸との間の線接触を可能にしている。その接触部位は、軸に直接形成されるか、あるいは有利には少なくとも部分的に、軸に結合された構造部品に設けられる。
【００１３】
接触部位の半径Ｒおよびディスクの厚さが、発生する軸方向力に適合される、ことが有利である。
【００１４】
本発明に基づく軸受装置によれば、軸方向力から生じ、特に歯車のはすばから生ずる傾斜姿勢が吸収され、軸間のスラスト軸受特にころ軸受から遠ざけられる。
【００１５】
以下図を参照して本発明を詳細に説明する。
【００１６】
第１軸２０は、ここでは一部しか示されていないシフトスリーブ２２を支持している。このシフトスリーブ２２は、中立位置から、紙面において「右側」に、第１軸２０と歯車２４との間でトルクを伝達する位置へ切り換えられる。その歯車２４は、変速機の第２常時かみ合い歯車である。第１軸２０は、回転中心線１２を中心として回転できる。歯車２４は、第１軸２０上に、ディスク２６によって、半径方向および軸方向に保持されている。ディスク２６は、軸方向の両側がそれぞれころ軸受２８、３０で包囲されている。これによって、ディスク２６は、従って歯車２４は、第１軸２０に対して自由に回転できる。ディスク２６は、軸方向において一方にころ軸受２８を介してまずディスク１０に接触支持されている。このディスク１０は、第１軸２０の段部（ラジアル面）３２に接している。
【００１７】
ディスク２６は、軸方向の反対側において、ころ軸受３０を介してまずディスク１４に接触支持されている。このディスク１４は、リング３４に接している。このリング３４は外周溝３６を有し、この外周溝３６に止め輪３８がはめ込まれ、この止め輪３８は、その周溝内を案内されている。リング３４は、軸方向でころ軸受３０と反対の側において、もう１つのころ軸受４０およびこれに隣接するディスク４２によって、保持されている。このディスク４２は、第１軸２０上に止め輪４４によって、固定されている。
【００１８】
リング３４は、その軸方向距離の一部にわたって、第２軸４６の内周面側に位置している。この第２軸４６も同様に、回転中心線１２を中心として回転できる。止め輪３８は、第２軸４６にある内周溝５０内に位置している。この内周溝５０の寸法は外周溝３６の寸法に相当している。第２軸４６はかみ合いクラッチ５４を支持し、このかみ合いクラッチ５４は、第２軸４６に固く（相対回転不能に）結合されている。
【００１９】
かみ合いクラッチ５４は、第１軸２０と第２軸４６との直接的なトルク伝達を可能にする位置に示されている。その場合、トルクは、第１軸２０から、この第１軸２０に固く結合されたシフトスリーブ２２および歯車２４を介して、まずかみ合いクラッチ５４に伝達され、そこから第２軸４６に伝達される。第２軸４６と（ここに一部しか示されていない）歯車５６とを結合するために、かみ合いクラッチ５４は、中立位置から、紙面において「右側」に移動させられる。
【００２０】
一方ではディスク１０と第１軸２０における段部（ラジアル面）３２との間の接触部位５８、および他方ではディスク１４とリング３４との間の接触部位６０は、半径Ｒで形成されている。その半径Ｒを、段部３２が一側に有し、リング３４が他側に、それぞれ有している。この半径Ｒによって、ディスク１０、１４との線接触が得られる。これらの接触線１６、１８は、それぞれ回転中心線１２を中心とする円となっている。
【図面の簡単な説明】
【図１】 本発明に基づく歯車用軸受装置付きの変速機の一部断面図。
【符号の説明】
１０ ディスク
１２ 回転中心線
１４ ディスク
１６ 接触線
１８ 接触線
２０ 第１軸
２２ シフトスリーブ
２４ 歯車
２６ ディスク
２８ ころ軸受
３０ ころ軸受
３２ 段部（ラジアル面）
３４ リング
３６ 外周溝
３８ 止め輪
４０ ころ軸受
４２ ディスク
４４ 止め輪
４６ 第２軸
５０ 内周溝
５４ かみ合いクラッチ
５６ 歯車
５８ 接触部位
６０ 接触部位
Ｒ 半径[0001]
The present invention relates to a gear bearing device described in the superordinate conceptual part of claim 1.
[0002]
In a transmission with a helical gear, the gear is loaded by an axial force caused by the helical. In particular, in the case of a transmission equipped with a large number of countershafts for load distribution, due to its axial force, it is arranged in the range between the input shaft and the main shaft supported by this input shaft in various operating conditions. In the second constant meshing gear, there is a problem that the bearing of this gear is deformed.
[0003]
In transmissions with multiple countershafts of the same shape for load distribution, gears arranged with a slight radial clearance on the input shaft or main shaft are supported radially by the gear arranged on the subshaft. Has been. However, in order to prevent these gears from moving from their axial position on their respective axes, they need to support the gears in the axial direction. However, the axial force from the helical will try to move the gear position in the axial direction.
[0004]
It is mainly divided into the following three operating states.
[0005]
First, torque is transmitted from the input shaft of the transmission to the countershaft via the first constant meshing gear in the first dangerous driving state. The thrust bearing is loaded relatively uniformly.
[0006]
However, axial forces are particularly disadvantageous in the other two operating conditions. First, the one operation state is an operation state in which torque is transmitted from the input shaft of the transmission to the countershaft via the second constant meshing gear. From there, torque is transmitted to any gear coupled to the main shaft. Another problematic operating condition is when the input shaft is coupled to the main shaft via first and second constant meshing gears and torque flows through both constant meshing gears to form a gear stage. Occur.
[0007]
The axial force generated in the former operating state acts to move the second constant meshing gear away from the input shaft in the axial direction. The axial force generated in the latter operating state acts to move the second constant meshing gear axially toward the input shaft. In either case, the axial force causes the thrust bearing of the second constant meshing gear to tilt.
[0008]
DE 196 32 281 discloses a thrust bearing for a second constant meshing gear. The disk used there is surrounded by roller bearings on both sides. The axial force tilts the disk and damages the roller bearings in the form of the peripheral holder, resulting in a significant reduction in bearing life.
[0009]
The subject of this invention is providing the bearing apparatus which removed the problem that a roller bearing inclines.
[0010]
This problem is solved by the means described in claim 1. Advantageous embodiments of the invention are described in the dependent claims.
[0011]
Based on the present invention, the first axis and the second axis are positioned coaxially and can be rotated at different rotational speeds to balance the axial force in the direction of the rotation center line of both the first and second axes. A first gear in a gear-type transmission, which is arranged on the means provided between the first thrust bearing and the second thrust bearing, in particular on the disc. In the bearing device for the gear in the range between the shaft and the second shaft, disks are provided between the first shaft and the first thrust bearing and between the second thrust bearing and the second shaft, respectively. The disc is in contact with each axis at a line, and the disc takes a posture perpendicular to the rotation center axis in a basic state, and on the one side around the perpendicular posture. Inclined posture and others It is configured to swing (sway) between side inclined posture is solved by.
In the expression before correction, the first axis and the second axis are coaxially positioned and can be rotated at different rotational speeds, and the axial force in the direction of the rotation center line of both the first and second axes. In a gear-type transmission, such that the gear is arranged on the means provided between the first thrust bearing and the second thrust bearing, in particular on the disc. In a bearing device for a gear in a range between a first shaft and a second shaft, disks are provided between the first shaft and the first thrust bearing and between the second thrust bearing and the second shaft, respectively. These discs are solved by making contact with their respective axes in a line and having a conical deformation movement about the contact line. Here, conical deformation movement means that a flat disk deforms into the shape of a conical annular plate under the action of an axial force, which is almost the same as a disc spring. It means to transform into a contour.
[0012]
In a preferred embodiment of the invention, radial and radial contact areas are formed on the first and second axes, which are the lines between the disc and the first and second axes. Enables contact. The contact site is formed directly on the shaft, or preferably at least partly on a structural part connected to the shaft.
[0013]
Advantageously, the radius R of the contact site and the thickness of the disc are adapted to the generated axial force.
[0014]
According to the bearing device according to the present invention, the tilting posture generated from the axial force, particularly from the helical gear, is absorbed and moved away from the thrust bearing between the shafts, particularly the roller bearing.
[0015]
Hereinafter, the present invention will be described in detail with reference to the drawings.
[0016]
The first shaft 20 supports a shift sleeve 22 that is only partially shown here. The shift sleeve 22 is switched from the neutral position to a position to transmit torque between the first shaft 20 and the gear 24 on the “right side” in the drawing. The gear 24 is a second constant meshing gear of the transmission. The first shaft 20 can rotate around the rotation center line 12. The gear 24 is held on the first shaft 20 by the disk 26 in the radial direction and the axial direction. The disk 26 is surrounded by roller bearings 28 and 30 on both sides in the axial direction. This allows the disk 26 and thus the gear 24 to rotate freely with respect to the first shaft 20. The disk 26 is first supported in contact with the disk 10 via a roller bearing 28 on one side in the axial direction. The disk 10 is in contact with a step portion (radial surface) 32 of the first shaft 20.
[0017]
The disk 26 is first supported in contact with the disk 14 via a roller bearing 30 on the opposite side in the axial direction. The disk 14 is in contact with the ring 34. The ring 34 has an outer circumferential groove 36, and a retaining ring 38 is fitted into the outer circumferential groove 36. The retaining ring 38 is guided in the circumferential groove. The ring 34 is held on the opposite side of the roller bearing 30 in the axial direction by another roller bearing 40 and a disk 42 adjacent thereto. The disk 42 is fixed on the first shaft 20 by a retaining ring 44.
[0018]
The ring 34 is located on the inner peripheral surface side of the second shaft 46 over a part of the axial distance. Similarly, the second shaft 46 can rotate around the rotation center line 12. The retaining ring 38 is located in the inner circumferential groove 50 in the second shaft 46. The dimension of the inner circumferential groove 50 corresponds to the dimension of the outer circumferential groove 36. The second shaft 46 supports a meshing clutch 54, and the meshing clutch 54 is rigidly coupled to the second shaft 46 (not relatively rotatable).
[0019]
The meshing clutch 54 is shown in a position that allows direct torque transmission between the first shaft 20 and the second shaft 46. In that case, the torque is first transmitted from the first shaft 20 to the meshing clutch 54 via the shift sleeve 22 and the gear 24 that are firmly coupled to the first shaft 20, and from there to the second shaft 46. . In order to couple the second shaft 46 and the gear 56 (only partially shown here), the meshing clutch 54 is moved from the neutral position to the “right side” in the drawing.
[0020]
On the one hand, the contact part 58 between the disk 10 and the step (radial surface) 32 in the first shaft 20 and on the other hand, the contact part 60 between the disk 14 and the ring 34 are formed with a radius R. The stepped portion 32 has one side of the radius R, and the ring 34 has the other side. With this radius R, line contact with the disks 10, 14 is obtained. These contact lines 16 and 18 are each a circle centered on the rotation center line 12.
[Brief description of the drawings]
FIG. 1 is a partial cross-sectional view of a transmission with a gear bearing device according to the present invention.
[Explanation of symbols]
10 Disc 12 Rotation center line 14 Disc 16 Contact line 18 Contact line 20 First shaft 22 Shift sleeve 24 Gear 26 Disc 28 Roller bearing 30 Roller bearing 32 Step (radial surface)
34 Ring 36 Outer peripheral groove 38 Retaining ring 40 Roller bearing 42 Disc 44 Retaining ring 46 Second shaft 50 Inner peripheral groove 54 Engagement clutch 56 Gear 58 Contact part 60 Contact part R Radius

Claims (3)

第１軸（２０）および第２軸（４６）が同軸的に位置すると共に互いに異なった回転数で回転でき、第１および第２の両軸（２０、４６）の回転中心線（１２）の方向における軸方向力をバランスするために歯車（２４）が配置され、この歯車（２４）が、第１スラスト軸受（２８）と第２スラスト軸受（３０）との間に設けられている手段（２６）上に配置されているような歯車式変速機における、第１軸（２０）と第２軸（４６）との間の範囲にある歯車（２４）に対する軸受装置において、
第１軸（２０）と第１スラスト軸受（２８）との間および第２スラスト軸受（３０）と第２軸（４６）との間に、それぞれディスク（１０、１４）が設けられ、これらのディスク（１０、１４）は、それぞれの軸（２０、４６）と線（１６、１８）で接触するようになっており、
前記ディスク（１０、１４）は、基本状態においては前記回転中心軸（１２）に対して垂直な姿勢を取る一方で、当該垂直な姿勢を中心として一方側傾斜姿勢と他方側傾斜姿勢との間で揺動するように構成されている
ことを特徴とする歯車式変速機の歯車用軸受装置。The first axis (20) and the second axis (46) are located coaxially and can be rotated at different rotational speeds, so that the rotation center line (12) of both the first and second axes (20, 46) A gear (24) is arranged to balance the axial force in the direction, this gear (24) being provided between the first thrust bearing (28) and the second thrust bearing (30) ( 26) In a gear transmission as arranged above, in a bearing device for the gear (24) in the range between the first shaft (20) and the second shaft (46),
Disks (10, 14) are provided between the first shaft (20) and the first thrust bearing (28) and between the second thrust bearing (30) and the second shaft (46), respectively. The disks (10, 14) are in contact with the respective axes (20, 46) at the lines (16, 18),
The discs (10, 14) take a posture perpendicular to the rotation center axis (12) in the basic state, and between the one-side inclined posture and the other-side inclined posture with the vertical posture as a center. A gear bearing device for a gear-type transmission, wherein the gear bearing device is configured to swing at a gear. 第１軸（２０）および第２軸（４６）に、所定の曲率半径（Ｒ）の接触部位（５８、６０）が形成され、これらの接触部位（５８、６０）が、ディスク（１０、１４）と第１、第２軸（２０、４６）との間の線接触を可能にしている
ことを特徴とする請求項１記載の歯車用軸受装置。Contact portions (58, 60) having a predetermined radius of curvature (R) are formed on the first shaft (20) and the second shaft (46), and these contact portions (58, 60) are formed on the discs (10, 14). And the first and second shafts (20, 46), the gear bearing device according to claim 1. 接触部位（６０）が、第２軸（４６）に結合された構造部品（３４）に設けられている
ことを特徴とする請求項２記載の歯車用軸受装置。3. The gear bearing device according to claim 2, wherein the contact part (60) is provided on a structural part (34) coupled to the second shaft (46).
JP2000569146A 1998-09-09 1999-09-03 Thrust bearing device for gears Expired - Fee Related JP4425469B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19841130A DE19841130A1 (en) 1998-09-09 1998-09-09 Axial bearing for gears
DE19841130.8 1998-09-09
PCT/EP1999/006495 WO2000014432A1 (en) 1998-09-09 1999-09-03 Axial bearing for toothed wheels

Publications (2)

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JP2002524704A JP2002524704A (en) 2002-08-06
JP4425469B2 true JP4425469B2 (en) 2010-03-03

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EP (1) EP1110013B1 (en)
JP (1) JP4425469B2 (en)
BR (1) BR9913521A (en)
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WO (1) WO2000014432A1 (en)

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Publication number Priority date Publication date Assignee Title
DE19841130A1 (en) * 1998-09-09 2000-03-16 Zahnradfabrik Friedrichshafen Axial bearing for gears
DE102004057126A1 (en) * 2004-11-26 2006-06-08 Zf Friedrichshafen Ag Device for reducing the axial movement of the main shaft wheels in a transmission with at least two countershafts
DE102004057124A1 (en) * 2004-11-26 2006-06-08 Zf Friedrichshafen Ag Device for reducing the movement of the main shaft
DE102008000822B4 (en) * 2008-03-26 2020-01-09 Zf Friedrichshafen Ag Device for reducing rattling noises in step gears
WO2017015737A1 (en) 2015-07-27 2017-02-02 Chris Lintaman Length-adjustable shoe
EP3222863A1 (en) 2016-03-22 2017-09-27 Siemens Aktiengesellschaft Bearing arrangement

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE325353C (en) 1920-09-11 Wolf Fackenheim Exchangeable attachment of the cutting iron on pocket lighters
DE709768C (en) * 1935-09-25 1941-09-01 Demag Akt Ges Resilient shaft bearing
DE707768C (en) 1937-07-08 1941-07-03 Siemens Schuckertwerke Akt Ges Impeller for impeller pumps
GB889871A (en) 1958-03-11 1962-02-21 Dowty Hydraulic Units Ltd Improvements in axial thrust bearings
US3829181A (en) 1972-03-14 1974-08-13 Skf Ind Trading & Dev Combined axial radial bearing
FR2222895A5 (en) * 1973-03-21 1974-10-18 Nadella
DE2908016A1 (en) * 1979-03-01 1980-09-11 Schaeffler Ohg Industriewerk Outer race for single row ball bearing - has cylindrical wall with bore acting as track for balls supported axially by spring-loaded ring
US5390561A (en) 1993-05-20 1995-02-21 Eaton Corporation Compound transmission
DE19630803A1 (en) * 1996-07-31 1998-02-05 Zahnradfabrik Friedrichshafen Bearing for shaft in vehicle gearbox
DE19631063A1 (en) * 1996-08-01 1998-02-05 Zahnradfabrik Friedrichshafen Axial bearing in vehicle gearbox
DE19633282A1 (en) * 1996-08-19 1998-02-26 Zahnradfabrik Friedrichshafen Vehicle gearbox
DE19633281A1 (en) * 1996-08-19 1998-02-26 Zahnradfabrik Friedrichshafen Gear box has co-axial first and second shafts allowing for simultaneous rotary
DE19633279A1 (en) * 1996-08-19 1998-02-26 Zahnradfabrik Friedrichshafen Vehicle gearbox with helical teeth
DE19841130A1 (en) * 1998-09-09 2000-03-16 Zahnradfabrik Friedrichshafen Axial bearing for gears

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EP1110013A1 (en) 2001-06-27
WO2000014432A1 (en) 2000-03-16
JP2002524704A (en) 2002-08-06
US6463822B1 (en) 2002-10-15
DE19841130A1 (en) 2000-03-16
EP1110013B1 (en) 2001-12-05
BR9913521A (en) 2001-06-05

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